US20150240805A1

US20150240805A1 - High-Pressure Pump for Use in a High-Pressure Press

Info

Publication number: US20150240805A1
Application number: US14/188,805
Authority: US
Inventors: David R. Hall; Scott Dahlgren
Original assignee: Novatek IP LLC
Priority date: 2013-02-26
Filing date: 2014-02-25
Publication date: 2015-08-27
Also published as: US20180163720A9; US10578100B2

Abstract

A high-pressure pump comprising an elongated casing and a hollow interior formed along a central axis thereof. At least one partition may be axially fixed within the elongated casing such that it divides the hollow interior. First and second pressure differential devices may be disposed on opposite sides of the at least one partition and each have a rotary shaft extending there through. A first rotary shaft extending through the first pressure differential device may be axially fixed by the at least one partition and rotationally fixed to a second rotary shaft extending through the second pressure differential device. The high-pressure pump may be driven by a servomotor and used in a high-pressure press.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This patent application claims priority to U.S. Provisional Pat. App. Nos. 61/769,602, filed on Feb. 26, 2013, and 61/772,757, filed on Mar. 5, 2013, which are incorporated herein by reference for all that they contain.

BACKGROUND OF THE INVENTION

The present invention relates generally to high-pressure pumps as are common in applications that use a high-pressure, high-temperature press, such as the manufacture of polycrystalline diamonds. More particularly, the present invention relates to high-pressure pumps that comprise a plurality of positive displacement pumps that are stacked to increase the overall pressure differential capabilities of the high-pressure pump. For example, a positive displacement pump may be able to generate only a limited pressure differential; when a higher pressure differential is desired, additional positive displacement pumps may be stacked to increase the overall pressure differential without exceeding the maximum allowable pressure differential across any solitary positive displacement pump.
Rotary gear pumps are well known types of positive displacement pumps employed to pump fluids from one location to another. Rotary gear pumps conventionally employ two gears having meshing teeth disposed within a housing to deliver fluid entering the housing from an inlet to an outlet. One of the toothed gears may be a drive gear rotated by a motor or other suitable means while the other gear may be a driven gear which is driven by the drive gear. An example of such a rotary gear pump can be found in U.S. Pat. No. 6,123,533 to McBurnett which discloses a positive displacement pump including a drive gear meshed with an idler gear. However, only a limited pressure differential may be able to be generated across such a rotary gear pump.
It may be desirable to combine two or more such positive displacement pumps together, creating a multi-stage operation, to increase the final discharge pressure. U.S. Pat. No. 6,666,666 to Gilbert discloses a pump comprising multiple, axially stacked positive displacement pumps. The stacked pumps are arranged within an outer retaining barrel in one or more stages. Drive and idler shafts extend axially through each stacked component. The entire stack of sections and crossovers between stages can be fit into the bore of a tubular barrel, compressed sealably together and retained therein. However, when generating extremely high pressure differentials in a particular stacked section, the pressure differential may cause the shafts used to drive the rotors to be displaced.

BRIEF SUMMARY OF THE INVENTION

In one aspect of the present invention, an elongated casing may comprise a hollow interior formed along a central axis. At least one partition may be axially fixed within the elongated casing such that it divides the hollow interior. This may be accomplished by a variety of methods. In one method, the at least one partition comprises an expandable exterior surface that may remain retracted during insertion into the hollow interior of the elongated casing and then expand to fix the at least one partition to the casing. In other methods, the at least one partition may be axially fixed to the elongated casing by a locking element extending through an exterior of the elongated casing.
First and second pressure differential devices may be disposed on opposite sides of the at least one partition and each have a rotary shaft extending there through. A first rotary shaft extending through the first pressure differential device may be axially fixed by the at least one partition. This may be accomplished by a variety of methods. In one method, the first rotary shaft comprises at least one appendage protruding there from such that the appendage is axially constrained by the partition. A thrust bearing may also be disposed between the appendage and the partition.
The first rotary shaft may also be rotationally fixed to a second rotary shaft extending through the second pressure differential device. This may be accomplished by a variety of methods. One method may comprise a male spline end on the first rotary shaft mating with a female spline end on the second rotary shaft. An alternative method may comprise the first and second rotary shafts mating through a coupling.
In some embodiments, the first rotary shaft drives a first parallel rotary shaft also extending through the first pressure differential device. The first parallel rotary shaft may also be axially fixed by the at least one partition. This may be accomplished by at least one appendage protruding from the first parallel rotary shaft and axially constrained by the partition. It may be necessary to offset the appendage of the first parallel rotary shaft from the appendage of the first rotary shaft. The first parallel rotary shaft may also be rotationally fixed to a second parallel rotary shaft extending through the second pressure differential device.
In various embodiments, the first and second pressure differential devices may each comprise either a solitary positive displacement gear pump or a plurality of positive displacement gear pumps. Fluid may pass from the first pressure differential device to the second pressure differential device through a channel in the at least one partition. The first and second pressure differential devices may be axially fixed within the elongated casing. At least one pressure transducer may extend through the elongated casing into the hollow interior. In some embodiments, the first rotary shaft may be connected to and driven by a servomotor.
In another aspect of the present invention, a high-pressure press may comprise a piston enclosing an expandable cavity. A bi-directional high-pressure pump may fluidly connect the expandable cavity to a reservoir. The bi-directional high-pressure pump may be capable of feeding fluid to the expandable cavity from the reservoir and also withdrawing fluid from the expandable cavity back to the reservoir. A servomotor may be used to control the bi-directional high-pressure pump. The bi-directional high-pressure pump may comprise a first rotary shaft axially fixed to a casing and rotationally fixed to a second rotary shaft. This may allow for a stack of pressure differential devices to build up pressure in the bi-directional high-pressure pump while preventing axial displacement of the rotary shafts.
In various embodiments, the high-pressure press may comprise a position transducer to identify the position of the piston or a pressure transducer to identify a pressure in the expandable cavity. A controller may receive input from the piston position transducer or expandable cavity pressure transducer to control the servomotor. In some embodiments, the high-pressure press may comprise a plurality of pistons operated simultaneously to compress a single chamber.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram of an embodiment of a high-pressure press comprising bi-directional high-pressure pumps fluidly connecting a reservoir to expandable cavities of several pistons.

FIG. 2 is a diagram of an embodiment of a high-pressure press comprising a bi-directional pump controlled by a servomotor.

FIG. 3 is a perspective view of an embodiment of a positive displacement gear pump.

FIG. 4 is a perspective view of an embodiment of a pressure differential device comprising a plurality of positive displacement gear pumps.

FIG. 5 is a longitudinal section view of an embodiment of a high-pressure pump.

FIG. 6 is a magnified longitudinal section view of an embodiment of a high-pressure pump.

FIG. 7 a is a perspective view of a first rotary shaft, a second rotary shaft and a coupling.

FIG. 7 b is a perspective view of an embodiment of a first rotary shaft comprising a male spline end and a second rotary shaft comprising a female spline end.

FIG. 8 is a longitudinal section view of an embodiment of a high-pressure pump comprising a pressure transducer.

FIG. 9 is a longitudinal section view of an embodiment of a high-pressure pump comprising locking elements extending through a casing.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the figures, FIG. 1 is a diagram of an embodiment of a high-pressure press 100 such as may be used to manufacture polycrystalline diamonds. In such operations, diamond grains may be mixed with catalyst, disposed in a canister and pressed under high pressure which allows for crystalline formation to sinter the grains together. Several canisters may disposed within a cube 110 placed between a plurality of pistons 120. Each of the plurality of pistons 120 may enclose an expandable cavity 130. Bi-directional high-pressure pumps 140 may port fluid back and forth between a reservoir 150 and each expandable cavity 130 to accurately extend and retract the plurality of pistons 120, thus applying pressure to cube 110.
FIG. 2 is a diagram of another embodiment of a high-pressure press 200. A servomotor 260 may provide precise control for a bi-directional high-pressure pump 240 that may port fluid back and forth between a reservoir 250 and an expandable cavity 230 of a piston 220. In various embodiments, the servomotor 260 may receive feedback from either a position transducer 270 (such as a linear variable differential transformer) identifying a position of the piston 220 or a pressure transducer 280 identifying a pressure in the expandable cavity 230.
In practice, if the pressure transducer 270 measures a deficiency in pressure in the expandable cavity 230, the servomotor 260 may receive a feedback signal to operate the bi-directional high-pressure pump 240 to move fluid to pressurize the piston 220. Alternatively, if the position transducer 270 measures an undesirable position for the piston 220, the servomotor 260 may receive a feedback signal to operate the bi-directional high-pressure pump 240 to move fluid to reposition the piston 220. Unlike prior art systems that require a perpetually running motor to maintain fluid pressure, this servomotor 260 may be shut off if the pressure is to be held constant.
FIG. 3 shows an embodiment of a positive displacement gear pump 300. The positive displacement gear pump 300 may comprise a substantially cylindrical body 310 comprising a fluid inlet 320 and a fluid outlet 330. The fluid inlet 320 and fluid outlet 330 may be separated by a gear chamber 340 in which a pair of complementary gears 350 may be disposed. The pair of complementary gears 350 may prevent fluid from passing through the gear chamber 340 from the fluid inlet 320 to the fluid outlet 330. The pair of complementary gears 350 may comprise a drive gear 355 and a driven gear 356, such that the driven gear 356 rotates in a direction opposite to the direction of rotation of the drive gear 355.
When the drive gear 355 is actuated, a fixed amount of fluid is transported from the fluid inlet 320 to the fluid outlet 330 according to the rotation of the drive gear 355 and the driven gear 356. The pair of complementary gears 350 may be formed in any practical manner and from any convenient material known to persons skilled in the art, e.g. such as those used in conventional hydraulic gear pumps. Various modifications to provide deviations from ordinary tooth profiles may be made to obtain a higher efficiency and reduced pressure pulses and noise.
When the drive gear 355 is rotated in a reverse direction, fluid is transferred from the fluid outlet 330 to the fluid inlet 320. Thus the positive displacement gear pump 300 may be bi-directional.
FIG. 4 shows an embodiment of a pressure differential device 400 comprising a plurality of stacked positive displacement gear pumps 403. Each of the plurality of stacked positive displacement gear pumps 403 may create a pressure differential there across. The pressure differentials across each of the plurality of stacked positive displacement gear pumps 403 may add to the total pressure differential attainable across the pressure differential device 400. The pressure differential device 400 may further comprise a drive shaft 455 and a driven shaft 456 extending there through, parallel to a central axis thereof. The drive shaft 455 may rotate a plurality of drive gears (hidden) within each of the plurality of stacked positive displacement gear pumps 403 which may each be rotating driven gears (hidden) that together rotate the driven shaft 456.
As the total pressure differential attainable across the pressure differential device 400 increases, so does the force required to hold the plurality of stacked positive displacement gear pumps 403 together and to keep the drive shaft 455 and driven shaft 456 axially constrained.
FIG. 5 shows an embodiment of a high-pressure pump 500 comprising a plurality of pressure differential devices 504 disposed within an elongated casing 510. The elongated casing 510 may comprise a substantially hollow interior 515 formed along a central axis thereof. At least one partition 520 may be axially fixed within the elongated casing 510 such that it divides the hollow interior 515. This may be accomplished, in various embodiments, by threading the at least one partition 520 within the hollow interior 515 or inserting the at least one partition 520 into the hollow interior 515 and then expanding an exterior surface thereof First and second pressure differential devices, 525 and 526 respectively, may be disposed on opposite sides of the at least one partition 520. A first rotary shaft 555 may extend through the first pressure differential device 525 and be axially fixed by the at least one partition 520. The first rotary shaft 555 may also be rotationally fixed with a second rotary shaft 556 extending through the second pressure differential device 526.
In some embodiments, the first rotary shaft 555 drives a first parallel rotary shaft 565 also extending through the first pressure differential device 525. The first parallel rotary shaft 565 may also be axially fixed by the at least one partition 520 and rotationally fixed to a second parallel rotary shaft 566 extending through the second pressure differential device 526.
This configuration may be desirable because the overall pressure differential across the high-pressure pump 500 is sustained by the casing 510. Each rotary shaft only bears the pressure associated with its corresponding pressure differential device. This allows extremely high pressure differentials to be achieved, as the casing 510 may be capable of withstanding higher pressures than any rotary shaft is able to withstand.
FIG. 6 shows a magnified view of a partition 620 axially fixed within an elongated casing 610 of a high-pressure pump 600. A first rotary shaft 655 may comprise at least one appendage 658 protruding therefrom. The at least one appendage 658 may be axially confined by the at least one partition 620 aided by a thrust bearing 659.
In some embodiments, the first rotary shaft 655 drives a first parallel rotary shaft 665. The first parallel rotary shaft 665 may also comprise at least one appendage 668 that is axially confined by the at least one partition 620 aided by a thrust bearing 669.
FIGS. 7 a and 7 b show embodiments of various shaft connection assemblies that may allow for rotational fixation without axial fixation. These types of connections may allow for torque to be transferred without transferring axial thrust. Specifically, FIG. 7 a shows first and second rotary shafts, 710 a and 720 a respectively, both comprising male spline ends that may mate with a female spline coupling 730 a. FIG. 7 b shows a first rotary shaft 710 b comprising a male spline end that may mate with a second rotary shaft 720 b comprising a female spline end.
FIG. 8 shows an embodiment of a high-pressure pump 800 comprising an elongated casing 810. Pressure transducers 890 may be disposed in holes 892 formed at various locations around the elongated casing 810 to allow for various pressure readings to be taken to monitor the pressures generated at different locations within the high-pressure pump 800. These pressure readings may be used to control the servomotor controlling the high-pressure pump.
FIG. 9 shows an embodiment of a high-pressure pump 900 comprising an elongated casing 910 with locking elements 990 extending there through to axially fix partitions 920 disposed therein.
Whereas the present invention has been described in particular relation to the drawings attached hereto, it should be understood that other and further modifications apart from those shown or suggested herein, may be made within the scope and spirit of the present invention.

Claims

What is claimed is:

1. A high-pressure pump, comprising:

an elongated casing comprising a hollow interior formed along a central axis;

at least one partition axially fixed within the elongated casing and dividing the hollow interior;

a first pressure differential device disposed on one side of the at least one partition and a second pressure differential device disposed on an opposite side; and

a first rotary shaft extending through the first pressure differential device, axially fixed by the at least one partition, and rotationally fixed to a second rotary shaft extending through the second pressure differential device.

2. The high-pressure pump of claim 1, wherein the first rotary shaft comprises a male spline end mating with a female spline end of the second rotary shaft.

3. The high-pressure pump of claim 1, wherein the first rotary shaft mates with the second rotary shaft through a coupling.

4. The high-pressure pump of claim 1, wherein each of the first and second pressure differential devices comprises a solitary positive displacement gear pump.

5. The high-pressure pump of claim 1, wherein each of the first and second pressure differential devices comprises a plurality of positive displacement gear pumps.

6. The high-pressure pump of claim 1, wherein the at least one partition comprises and is axially fixed by an expandable exterior surface.

7. The high-pressure pump of claim 1, wherein the at least one partition is axially fixed by a locking element extending through the elongated casing.

8. The high-pressure pump of claim 1, further comprising at least one pressure transducer extending through the elongated casing into the hollow interior.

9. The high-pressure pump of claim 1, wherein the first rotary shaft comprises at least one appendage protruding therefrom and axially constrained by the partition.

10. The high-pressure pump of claim 9, further comprising a thrust bearing disposed between the appendage and the partition.

11. The high-pressure pump of claim 9, wherein the first rotary shaft drives a first parallel rotary shaft also extending through the first pressure differential device, and axially fixed by the at least one partition, and rotationally fixed to a second parallel rotary shaft extending through the second pressure differential device.

12. The high-pressure pump of claim 11, wherein the first parallel rotary shaft comprises at least one appendage protruding therefrom and axially constrained by the partition, axially offset from the appendage of the first rotary shaft.

13. The high-pressure pump of claim 1, wherein the first rotary shaft is connected to and driven by a servomotor.

14. The high-pressure pump of claim 1, further comprising a channel wherein fluid may travel through the at least one partition.

15. The high-pressure pump of claim 1, wherein the first and second pressure differential devices are axially fixed within the elongated casing.

16. A high-pressure press, comprising:

a piston enclosing an expandable cavity;

a bi-directional high-pressure pump fluidly connected to the expandable cavity;

a reservoir fluidly connected to the bi-directional high-pressure pump; and

a servomotor controlling the bi-directional high-pressure pump;

wherein the bi-directional high-pressure pump comprises a first rotary shaft axially fixed to a casing and rotationally fixed to a second rotary shaft.

17. The high-pressure press of claim 16, further comprising a position transducer to identify a position of the piston.

18. The high-pressure press of claim 16, further comprising a pressure transducer to identify a pressure in the expandable cavity.

19. The high-pressure press of claim 16, further comprising a controller that receives input from a piston position transducer or expandable cavity pressure transducer to control the servomotor.

20. The high-pressure press of claim 16, further comprising a plurality of pistons operated simultaneously to compress a single chamber.